Shaping machine



G. DAVENPORT ET AL Feb. 2, 1965 SHAPING MACHINE 4 Sheets-Sheet 1 Filed Oct. 17, 1960 .INVENTORS. GRANGER DAVENPORT C IFF-02D E HEIMA LL flv'zopoee' R CROcKEE 41 M V ATToz/vEy' Feb.2, 1965 G. DAVENPORT ETAL I 3,

SHAPING MACHINE Filed Oct. 17, 1960 4 Sheets-Sheet 2 MoToR RUN STOP /r/ a B 4 L11. 3 l 90 v nwz'm'ons.

GRANGER DAVENPORT a Dc Cur-r020 E HEIMALL {BRAKE THEODORE IE CEOCKEE jSgNTROL Y'Z 3 ATTO ENE Y Feb. 2, 1965 G. DAVENPORT ETAL 3,168,005

SHAPING MACHINE Filed Oct. 17, 1960 4 Sheets-Sheet 3 INVENTORS. GEA NGER DA VEN PORT C1. IFFOED E. HEIMALL THEo DORE I2 CEOCKEE A TT'OIENEY Feb. 2, 1965 s. DAVENPORT ETAL 3,158,005

SHAPING MACHINE Filed Oct. 17, 1960 4 Sheets-Sheet 4 PRESSUR'IZED MACHINE LU BRICATING SYSTEM NTORS GRANGER wml bm' C1. I FFORD E. HEIMALL T115000 es RCRQCKER ATTOR NEY United States Patent Ofifice 3,168,905 Patented Feb. 2, 1965 This invention relates to improvements in machine tools and their drive transmissions and more particularlyto an improved method and means for operating a shaping machine.

The conventional shaper comprises a box-like frame with horizontal guideways along its top and vertical guideways along its front. A crossrail member having horivzontal work-table-carrying guideways along its front is mounted on the vertical guideways of the frame and a tool-carrying ram member is mounted for reciprocation on the top guideways of the frame. The work piece to be machined is mounted on the work table and on each forward stroke of the ram the tool carried at its forward end engages the work and planes or shapes off a portion thereof. On the return stroke of the ram, the Work table is propelled laterally or vertically as the case may be, a unit increment so that on succeeding forward strokes of the ram the tool operates successively upon new areas of the work piece. When the work surface has been machined to the required extent, the work table is backtraversed to the point of starting and the cycle is repeated upon the same or another work piece.

In the earlier types of shapers the machine was driven by overhead belts and started and stopped by shifting the drive belt. Later, an electric motor mounted on the machine operated through a main friction-type clutch to drive the machine. The clutch was designed for manual operation and considerable effort was required to operate it to bring the machine to a stop. It was also common practice to equip the shaper with a lubricating pump that received power from the motor at a point ahead of the main friction clutch. Hence, whenever the motor was started, the pump was driven continuously and furnished lubricant to the numerous gears and elements in and upon the main frame before the clutch was engaged to drive the machine. For a few years it was popular to take power from the continuously running pump drive to operate the work table feed screws selectively at a traverse rate, usually in a direction opposite the intermittent feed that came from the ram drive train, so that the work could be back-traversed quickly to the starting point.

Considerable difiiculty was, and continues to be, experienced with friction-clutch drives, one difficulty being the inability of the clutch to pick up the load in the event the operator has stalled the tool in the cut, and another being that the inertia of the ram tends to drive the clutch backwards on each ram reversal with consequent destructive effects upon the clutch. Increasing the size of the clutch did not provide an answer, for that not only created bulky design problems, but resulted in too great a jolt to the machine whenever the clutch engaged.

The main purpose and objective of this invention is not only to provide a practical solution to the perplexing problems that exist with the use of friction clutches in shaper drives, but to increase the efficiency of the shaping machine by the development of an improved drive and operational method. A further aim of the invention is to render available a shaping machine wherein ram speeds and work table movements are more easily controllable, as for example, by pushbuttons that require a minimum effort on the operators part for their actuation. Still another aim of the invention is to provide a machine in which the full power of the drive motor is available at all times to propel the ram and to propel the work table incrementally. The invention has for a further object, the provision of a machine-tool transmission in which the clash ing of teeth of shiftable gears is reduced to minimum proportions. Most of the time the teeth of shiftable gears will line up or find themselves on shifting. Occasionally and notwithstanding the rounding of the leading ends of the teeth, a set of gears will meet dead on. If there is a main clutch in the drive, the instantaneous start incident to the engagement of a clutch with a running motor causes the gears to spin, producing considerable noise and eventually severe damage. However, if in accordance with the basic features of this conception of a machine-tool drive, a main clutch is not used, and the main motor is directly connected to the ram, the restarting of a stopped motor provides just enough delay in starting to allow the teeth of the gears to mesh properly before the motor reaches its normal running speed. The use of a direct-connected main-drive motor also makes possible the conception and provision of an auxiliary motor to drive a lubricating pump that will supply lubricant to needed areas and furnish hydraulic pressure to actuate hydraulic gear-shifting cylinders and clamp, etc. To advantage, the auxiliary motor may be operatively connected also to the work table feed trains to traverse the table up or down, or to the left or right, while the main motor stands idle and the main transmission is immobilized. Motor controls are arranged, as will more fully appear, so as always to cause the auxiliary motor to start operating before the main motor that drives the ram is energized. This conception has the objective of insuring adequate lubrication and pressure in the hydraulic gear-shifting system and hydraulic clamps or the like before the main shaper drive is started.

In carrying forward the aims and objectives of this invention, a new shaper design is proposed in which the main motor is built-in within the main frame and directly and permanently connected With the change-speed gearing of the ram-drive and work-table-feed transmissions. The main motor is preferably provided with a magnetic brake or equivalent means to overcome armature inertia and obtain almost instantaneous stopping when the starter switch for the main motor drops out. In conjunction and in combination a second motor is provided, built-in like the main motor, which is permanently connected with an hydraulic pump and also connected to a selector clutch in the work table feed trains. The arrangement is such that the auxiliary motor is continuously available for traverse movements of the work table while the main motor is available only for the intermittent feed movements of the work table. In this connection it may be said that this conception comprehends a system of gearing arrangements in which the rapid traverse movements of the work occur in directions that are always opposite to that of the feed regardless of the direction of the feed. L1 other words, when the intermittent feed train is disconnected and the traverse train is connected to the tabledrive element, the table and work thereon always moves away from the cutting tool carried by the ram whether the drive train to the latter is operating or not, provided, of course, the operator does not purposely change the direction of movement by shifting the direction-control lever.

Other objects and advantages Will be in part indicated in the following description and in part rendered apparent therefrom in connection with the annexed drawings.

To enable others skilled in the art so fully to comprehend the underlying features hereof that they may embody the same in the various ways contemplated by this invention, drawings depicting a preferred typical construction have been annexed as parts of this disclosure and, in

such drawings, like characters of reference denote corresponding parts throughout all the views, of which:

FIG. 1 of the drawing is a side elevation of a shapin machine embodying this invention,

FIG. 2 is a fragmentary plan view of two portions or the driving transmission including the main and auxiliary motors and their control circuitry schematically,

FIG. 3 is a development of the gearing of the main and auxiliary transmission of the machine, and

FIG. 4 is a schematic representation of the hydraulic system.

Referring more particularly to FIG. 1, the shaping machine represented thereby comprises a substantially hollow box-like frame member 10, that has dovetail guideways 11, along its upper surface and vertical rectangular guideways 12 along its front surface. The shaper ram, indicated at 13, is provided with guides that fit the frame guideways and carries at its forward end the conventional vertically and angularly adjustable toolhead that is adapted to mount a tool T in the usual manner.

A crossrail 14 is fitted to the vertical guides of the frame and is equipped with horizontal guideways 15 that receive mating portions of a work table supporting slide 16. The slide 16 mounts work table 17 in a conventional manner, and which may have clamped thereto a work fixture 17a for supporting the work piece W to be operated upon.

In normal shaping-machine operations the work W is clamped in position and the crossrail 14 elevated on the guides 12 to bring the surface to be operated upon within the range of vertical adjustment of the tool T, and the crossrail is there clamped by means of a lever 20. The reciprocatory stroke of the ram 12 is adjusted to suit the length of the cut to be made on the work, and the tool T is lowered by operation of hand crank 21 until the tool begins to cut. On the forward stroke or the ram the work and work table remain stationary and on the return stroke of the ram the work and work table are fed l'aterally along the crossrail 14 a unit distance so that on the next forward stroke of the ram the tool T will operate upon a new area of the work. The magnitude of the lateral feed increment is of course adjustable to suit the operation. After the desired total distance of intermittent lateral feed of the work has been attained, the intermittent feed train is disconnected and the traverse train is engaged to propel the work laterally at a traverse rate back to the point of starting. If it is necessary, the tool T is lowered a preselected distance and the ram and inthe initial shaft 25 of a primary set of speed-change gears by means of the pulleys and V-belts 24. The primary set of change gears provides eight relatively fine changes in speed and includes shafts 26, 27, and 28 each of which has secured and/ or splined thereto, one or more sets of cluster gears. Shaft 25 carries a two-gear cluster 25a selectively engaged by an axially shiftable set of cluster gears 26b splined on shaft 26. Shaft 26 also mounts a two-gear cluster 26a that meshes with a shiftable set of cluster gears 27b splined on shaft 27. Shaft 27 also mounts a slidable cluster 27b that meshes with gears of cluster 28a on the shaft 28. It will be seen from FIG. 3 that the shiftable cluster gears 26b, 27b, and 27b are in pairs and more closely spaced than the gears 25a, 26a, and 28a of the nonshiftable clusters so that not only can only one pair of mating gears of cooperating clusters be engaged at any onetime, but that space is provided to permit complete withdrawal of one gear fromits mate before the other gear of the cluster can engage its mate. The shiftable gears of the change-speed gearing are, in this embodiment of the invention, shifted laterally from one engaged position to the other engaged position, by means of two-way-acting hydraulic cylinders 26c, 27c, and 270' illustrated in FIG. 4. The piston rods positioned by the hydraulic cylinders are indicated respectively at 26p, 27p, and 27p, each carrying a yoke piece that straddles its associated cluster. The hydraulic cylinders receive fluid under pressure at one end or the other as required and are controlled by a selector valve SV in a manner believed unnecessary to be described in detail for explanation of this invention. Suffice it to mention that when a given shift cylinder is operated it moves its connected gear cluster directly from one engaged position to its other engaged position, that is, there is no neutral or intermediate stopping position. Accordingly, shaft 28 is continuously running whenever the main motor M1 is running.

Shaft 28 carries a wide-faced pinion 29 that meshes continuously with one of the gears of a two-gear shiftable cluster 30 that forms part of a secondary change-speed set. The gears of the cluster 30 are shifted hydraulically by means of a piston rod 30p actuated by hydraulic cylinder 30c and carrying a yoke piece straddling the cluster 30 and are adapted to mesh selectively with the large bull gears 31. Gears 31 have a main axle 32, journalled in the main frame of the machine, and parallel guides across their inner end face that support and guide a radially adjustable crank pin 33. The crank pin revolves in a bearing block that is slidably fitted to a slot in the ram-driving pitman lever 34 shown in FIG. 1. Lever 34 is pivoted at its lower end 34a to the main frame and is linked as at 34b to theram 13 at its upper end. As with the shiftable clusters of the primary change-speed gears, the shiftable cluster 30 of the secondary set has two effective positions without a neutral or intermediate position. Hence whenever the main motor M1 is running, the bull gears are rotating and the ram 13 is being reciprocated.

Power to feed the work table unit increments laterally or vertically is derived from the axle of the bull gears through gearing 35 and ratchet mechanism indicated generally at 35a which functions to give a feed increment on the return or back stroke of the ram.

A clutch 36, controlled by a handle 37, is provided to connect the intermittent motion of the ratchet mechanism to a shaft 38 that in turn is connected by bevel gears 39 to a forwardly extending splined shaft 40. The f0rward end of the shaft 40 is journalled in the crossrail 14 and moves vertically therewith. Through a bevel gear reverser 41, controlled by clutch handle 42, the power of shaft 40 is transmitted, in either direction, to shaft 43 and thence through a selector clutch 45 to either the crossfeed train 46 or the table-elevating train 47. The crossfeed train 46 includes a clutch gear 46a that meshes; with a gear 46b on a screw shaft 460. .The screw shaft 460 is journalled against endwise movement in the crossrail 14 and threads a nut 16a that is secured to the table: carrying cross-slide 16. The vertical-feed train includes: clutch gear 47a, idler gear 47b, worm-shaft gear 470,. worm shaft 47d, and worm gearing 472. The worm gearing 472 comprises a rotatable nut that threads a stationary shaft 47 The nut is rotatable but not trans-- latably journalled in the vertically movable crossrail 14..

The foregoing briefly explains the intermittent feed trains of the work table by which the work is advanced incrementally between the working strokes of the ram to successively present new Work areas to the cutting tool. The intermittent feed, is, it will be observed, operative only when the ram is in motion. In prior shaping-machine drives, power to traverse the table quickly to a starting position was also taken from the axle 32 of the bull gears through gearing or chain drive means that by-passed the ratchet-feed mechanism 35. With such arranger chain and sprockets 50 drives a jack shaft 51.

ments, however, the ram is reciprocating whenever the operator desires to return the work table quickly or move it to the approximate working position quickly, an arrangement which is not only hazardous to theoperator, but harmful to the machine should the table be shifted untimely or too far.

With the present invention such dangers are avoided by the provision of a separate motor for work table traverse and hydraulic pump operations with safety controls interlocked with the controls of the main motor to insure proper lubrication and hydraulic pressure available for shifting gears even through the main motor may be stopped. This separate motor drive is best illustrated in FIG. 3 and comprises motor M2 which through a The jack shaft 51 is connected through a chain 52 and sprockets to a continuously operating pump P and also through a chain 53 and sprockets with a shaft 54. Shaft 54 drives through a chain 55 and sprockets another shaft 56 wfn'ch in turn drives through a chain '57 a clutch sprocket 58 that is loose on the shaft 38. When the feed-traverse clutch 36 is shifted from the feed-engaged position illustrated in FIG. 3 to a position that engages the clutch sprocket 58, the intermittent feed is disconnected, and

the rapid traverse is engaged. Continuous power from the separate motor M2 then fiows through shaft 38, gears 39, and'forwardly extending shaft 40 to the crossrail in the manner previously explained in connection with the intermittent feed where is may be employed selectively to shift the rail 14 up or down, or the table slide 16 laterally in either direction. It is to be mentioned here that whenever the feed-traverse clutch 36 is shifted from feed position to traverse position the resulting continuous motion imparted to the crossrail or to the cross slide is always opposite the direction to the direction imparted by the intermittent feed mechanism 35, unless clutch handle 42 is shifted concurrently.

Referring more particularly to FIG. 4, this drawing provides a schematic representation of the relationship between the hydraulic pump P driven by the motor M2 and components of the shaping machine related particularly to the instant invention, which are supplied with pressurized fluid by the pump P.

Since pressurized lubricating systems for machines are well known and since the details of such a system form no part of the instant invention, the pressurized machine lubricating system as illustrated in FIG. 4 merely includes a schematic representation of conduits for deliveringpressurized lubricating fluid to the gear trains and thence to the sump 101. However, it is to be understood that the pressurized machine lubricating system may also include conventional arrangements for the distribution of lubricating fluid to other portions of the shaping machine which require lubrication.

FIG. 4 also includes a schematic representation of the operative relationship between the selector valve SV described above and the two-way-acting hydraulic cylinders 26c, 27c, 27c, and 300 operable in the manner described above to displace the respective gear clusters by displacement of the piston rods 26p, 27p, 27p, and 30p, respectively.

While the pump P may also supply pressurized fluid to hydraulically actuated clamps, as noted above, this feature is not illustrated in FIG. 4, because such arrangements are well known and form no part of the instant invention.

Controls The circuitry for the main and auxiliary motors and their controls is illustrated diagrammatically in FIG. 2. Power lines L L L enter the machine through a main switch MS andcircuit breaker CB and have leads connecting motor starter relays 1M and 2M in parallel. Additional leads connect with a transformer TT which reduces the line voltage to that suitable and safe for control circuits. On the output side of'the transformer an indicator light is connected that lights up whenever the main switch is closed.

To start the auxiliary motor M2 for traversing the work table and to supply lubrication and oil under pressure for operating the hydrauiically operated elements of the machine, a spring-centered selector switch SS2 is rotated counterclockwise from its neutral position and then released. This allows current to flow momentarily through contacts A and B of the switch SS2 and through line 71 to contacts C of a second switch SS1. With switch SS1 in STOP position, current is supplied by line 73 to motorstarting relay 2M and the motor switch closes. Simultaneously, current in line 73 passes through a normally closed limit switch 1LS to a time delay switch TR2. Energizing relay 2M establishes a holding circuit, lines 73, 74, and 75 for the coils of relay 2M and timer TR2.

Energization of the coil of timer TR2 does not result in a closing of its normally open contacts immediately, but initiates a timing cycle of relatively short duration, after which the contacts close. This closing of the timer contacts completes a portion of the circuit to the coil of the main-motor starter relay 1M. The circuit to relay 1M may thereafter be completed by moving the control handle of switch SS1 to RUN position. Movement of the switch SS1 of main motor M1 to RUN position allows current to flow from line L1 through the contact A of switch SS2, line 74, the now closed contacts of relay 2M, line 75, line 77, switch SS1, the now closed contacts of the timer TR2, line '76, starter or relay coil 1M to line L2. Thus it will be seen that the ram-driving motor M1 cannot be started unless the pump motor M2 has been first started and that the stopping of the auxiliary motor M2 by moving its switch SS2 to STOP position will automatically stop the ram-driving motor. It will also be noted that the ram-driving motor M1 cannot be started immediately after the motor M2 is started because the timer TR2 delays starting for a short interval suflicient to insure advance lubrication and hydraulic pressure in the various hydraulic clamping and gear-shifting systems. The ram-driving motor M1 may, of course, be stopped independently of the auxiliary motor M2 by moving the handle of switch SS1 to STOP position.

It will be seen in FIG. 2 that the relay 1M has a pair of normally closed contacts which opens when the relay is energized. When the relay 1M is not energized so that the main motor is stopped, A.-C. current from the line flows through the normally closed contacts of relay IM to a D.-C. brake control panel where it is converted to direct current and supplied through lines 78 and 79 to the coil of a magnetic brake BR on the main motor M1. Thus, when the main motor is stopped, the brake is ON, when the main motor is started the closed contacts of relay 1M open and the brake is OFF. Preferably a rheostat R1 is installed in the control panel to adjust the brake torque.

The limit switch 1L8 previously referred to in the circuit of the timing relay TR2, forms part of a selector valve assembly SV certain features of which are illustrated schematically in FIG. 2. Briefly, the valve SV includes a rotatable dial member by which the various speed changes may be selected by an axially shiftable clutch-type knob K. To change speeds, the knobK is depressed until it is clutched to the dial and then rotated to the speed selected. Details of the body structure of the valve SV and piping to the pump and the various hydraulic gear-shifting cylinders have been omitted in the interest of clarity, since the essential relationship is indicated schematically in FIG. 4. However, the normally closed limit switch 1LS is actuated to OPEN position whenever the knob K of the valve SV is depressed. Inasmuch as the limit switch 1LS is in the holding circuit of timing relay TR2, the latter will de-energize when the knob K is depressed, thereby opening the circuit to the coil of the relay 1M and the ram-driving motorwill stop. When the selected speed change has been accomplished by rotating the valve SV and the knob K is released, a spring returns the knob K to its de-clutched position allowing the limit switch 1LS to close and re-energize the timer relay TR2. After a short time delay, sufficient to allow the gears to shift, the contacts of relay TRZ close, which completes the circuit to the ram-drive-motor relay 1M and the ram motor starts again. The initial rate of acceleration of the motor M1 is low so that motor M2 rotates the gears slowly enough to permit the shift to completes its action, without clashing or spinning, if the teeth of the hydraulically shifted gears happen to meet dead-on. The clashing and eventual damage previously mentioned respecting shaper drives that include a main clutch and the rapid starts that are produced thereby are eliminated by this combination of a direct-connected main-drive motor and a separate motor for table traverse and pump operatiom Without further analysis, the foregoing will so fully reveal the gist of this invention that others can, by applying current knowledge, readily adapt it for various utilizations by retaining one or more of the features that fairly constitute essential characteristics of this invention by which it is distinguished from the prior art, and, therefore, such adaptations should be, and are intended to be,

comprehended within the meaning and range of equivalency of the following claims.

What is claimed is:

1. In a shaping machine having a ram reciprocably mounted thereon and a work table movably mounted thereon, the combination of a main-drive motor, continuously operative driving connections between the maindrive motor and the ram operative to reciprocate the ram whenever the main-drive motor is operating, said continuously operative connections including selectively shiftable change-speed gear, manually controlled hydraulically operated means operatively connected with the changespeed gearing for shifting the gearing to obtain any one of a plurality of different ram speeds with the maindrive motor not operating, a pump for supplying fluid 'under pressure for actuating said hydraulically operated means, and a separate motor with continuously operative driving connections to the pump for driving said pump operable'independent of the operation of the main-drive motor.

2. In a shaping machine having a ram reciprocably mounted thereon, the combination of amain-drive motor, continuously operative driving connections between the main-drivemotor and the ram operative to reciprocate the ram whenever the main-drive motor is operating, said .continuously operative connections including selectively .shiftable change-speed gearing, manually controlled hydraulically operated means operatively connected with the change-speed gearing for shifting the gearing to obtain .any one of a plurality of different ram speeds, a pump for supplying fluid under pressure for actuating said hydraulically operated means, a separate motor for driving said. pump, and control means for said main-drive motor and for said separate motor, including a timing device operative automatically to delay the starting of said main-drive motor until after said separate motor is in 1 operation.

of a main-drive motor, continuously operative driving connections between the main-drive motor and the ram tent movement and an operative connection between the intermittent motion means and the shaping machine work table for propelling the table intermittently at a feeding rate, said last-mentioned connection including a selector clutch adapted when actuated to one effective position to render said intermittent motion means effective to propel the shaping machine work table at a feeding rate, and operative connections between said separate motor and said selector clutch operative when said clutch is shifted to another effective position to render said separate motor effective to propel the shaping machine work table at a traverse rate.

5. The combination of claim 4 including means including a limit switch in the control means for the said maindrive motor operative to stop the main-drive motor that drives the ram when the manually controlled hydraulically operated means is actuated to effect a change in ram speed.

6. In a shaping machine having a ram reciprocably mounted thereon and a work table movably mounted thereon, the combination of a main-drive motor, continuously operative driving connections between the maindrive motor and the ram operative to reciprocate the ram whenever the main-drive motor is operating, a pump for supplying fluid under pressure for lubricating the shaping machine and for operating hydraulically actuated elements of the shaping machine, a separate motor operable independently of the main-drive motor, continuously operative driving connections between said separate motor and the pump for driving said pump, means selectively operable to start and stop the separate motor, means selectively operable to start and stop the maindrive motor, means operable to preclude starting the main-drive motor until after the separate motor has been started, and means operable to stop the main-drive motor whenever the separate motor is stopped.

7. The combination of claim 6 additionally including intermittent motion producing means driven from the ramdriving connections with the main-drive motor for producing intermittent feeding movements, operative connections between said intermittent motion producing means and the shaping machine work table for advancing the work table intermittently between successive forward strokes of the ram, continuous motion producing means driven from the pump-driven connections with the separate motor for producing continuous traversing movements, operative connections between said continuous motion producing means and the shaping machine work table for traversing the work table, and a selector clutch effective in a first position to render said intermittent mo tion producing means operative on the work table and effective in a second position to render said continuous motion producing means operative on the work table.

8. In a shaping machine having a ram reciprocably mounted thereon, the combination of a pump for supplying fluid under pressure for lubrication and for actuating hydraulically operated elements of the shaping machine, an auxiliary motor, continuously operative driving connections between the auxiliary motor and the pump for driving said pump, a main-drive motor, continuously operative driving connections between the main-drive motor and the ram operative to reciprocate the ram whenever the main-drive motor is operating, said last-mentioned arose-o5 continuously operative connections including selectively shiftable change-speed gearing, hydraulically operated means operatively connected With the change-speed gearing for shifting the gearing to obtain any one of a plurality of different ram speetis, actuating means for said hydraulically operated means automatically effective to deenergize the main-drive motor whenever said hydraulically operated means are actuated, and means elfective to preclude energization of the main-drive motor except while the auxiliary motor is operating.

9. The combination of claim 4 additionally including means selectively o erable to start and stop the separate motor, means selectively operable to start and stop the main-drive motor, means operable to preclude starting the maimdrive motor until after the separate motor 1,579,651 Deale Apr. 6, 1926 2,344,434 Wigglesworth et a1 Mar. 14, 1944 2,349,382 Schreiber et al. May 23, 1944 2,599,388 Hicks June 3, 1952 10 2,664,497 Morrison July 22, 1952 OTHER REFERENCES Shapers, Smith & Mills Catalog 101N, Smith & Mills Shaper Division, Nebel Machine Tool Corporation, 34-01 15 Central Earkway, Cincinnati 25, Ohio, Recd in US. Patent Office Sept. 15, 1960. 

1. IN A SHAPING MACHINE HAVING A RAM RECIPROCABLY MOUNTED THEREON AND A WORK TABLE MOVABLY MOUNTED THEREON, THE COMBINATION OF A MAIN-DRIVE MOTOR, CONTINUOUSLY OPERATIVE DRIVING CONNECTIONS BETWEN THE MAINDRIVE MOTOR AND THE RAM OPERATIVE TO RECIPROCATE THE RAM WHENEVER THE MAIN-DRIVE MOTOR IS OPERATING, SAID CONTINUOUSLY OPERATIVE CONNECTIONS INCLUDING SELECTIVELY SHIFTABLE CHANGE-SPEED GEAR, MANUALLY CONTROLLED HYDRAULICALLY OPERATED MEANS OPERATIVELY CONNECTED WITH THE CHANGESPEED GEARING FOR SHIFTING THE GEARING TO OBTAIN ANY ONE OF A PLURALITY OF DIFFERENT RAM SPEEDS WITH THE MAINDRIVE MOTOR NOT OPERATING, A PUMP FOR SUPPLYING FLUID UNDER PRESSURE FOR ACTUATING SAID HYDRAULICALLY OPERATED MEANS, AND A SEPARATE MOTOR WITH CONTINUOUSLY OPERATIVE DRIVING CONNECTIONS TO THE PUMP FOR DRIVING SAID PUMP OPERABLE INDEPENDENT OF THE OPERATION OF THE MAIN-DRIVE MOTOR. 